CN102401011B - Bearing construction - Google Patents

Bearing construction Download PDF

Info

Publication number
CN102401011B
CN102401011B CN201110200275.6A CN201110200275A CN102401011B CN 102401011 B CN102401011 B CN 102401011B CN 201110200275 A CN201110200275 A CN 201110200275A CN 102401011 B CN102401011 B CN 102401011B
Authority
CN
China
Prior art keywords
inner ring
bearing
axle
face
inner race
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201110200275.6A
Other languages
Chinese (zh)
Other versions
CN102401011A (en
Inventor
石川司郎
冈龙太郎
上野正典
平泽义光
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2005119594A external-priority patent/JP2006300130A/en
Priority claimed from JP2005122812A external-priority patent/JP4731198B2/en
Application filed by NTN Corp filed Critical NTN Corp
Publication of CN102401011A publication Critical patent/CN102401011A/en
Application granted granted Critical
Publication of CN102401011B publication Critical patent/CN102401011B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F15/00—Axle-boxes
    • B61F15/20—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/10—Railway vehicles

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The invention provides a kind of bearing construction, it possesses: axle; Bearing inner race, it is embedded in described axle; Abutting member, it is connected to the end face of described bearing inner race, and is embedded in described axle, and the end face of described abutting member has the contacting part with the end contact of described bearing inner race at its radially inner side; At its radial outside, from the position that described contacting part retreats vertically, have not with the non-contact portion of the end contact of described bearing inner race, the radial width w of the end face of described bearing inner race 1, with the radial width w of described contacting part 2, there is w 2/ w 1the relation of≤0.5.

Description

Bearing construction
The divisional application that the application is the applying date is on April 5th, 2006, application number is 200680012884.6 (international application no: PCT/JP2006/307229), name is called the application of " roller bearing and bearing construction ".
Technical field
The present invention relates to roller bearing and bearing construction, particularly relate to roller bearing and the bearing construction of the axle supporting large bending moment effect.
Background technique
In the past, as the bearing supporting railway vehicle axle, often use the multiple row cone roller bearing at multiple row roller bearing and back side combination (hereinafter referred to as " outer synform ").
Because high effect of bearing a heavy burden during railway travels, rail truck axletree can bend relative to spin axis the so-called flexure simultaneously rotated to Vertical direction.Now, due to the small slip (hereinafter referred to as " wearing and tearing ") occurred between axletree and the bearing inner race of support axletree, there is the inner peripheral surface interfere in ends axletree of inner ring, thus the problem of scar (hereinafter referred to as " axle trace ") is produced at the outer circumferential face of axletree.
In the past, in order to avoid the problems referred to above, such as, the rail truck axletree support structure taking to implement countermeasure shown in Fig. 1 is known to.The multiple row cone roller bearing 1 supporting railway vehicle axle 10 possesses: two ends have the inner ring 2 of lip part; Outer ring 3; Be configured at the multiple row cone roller 4 between inner ring 2 and outer ring 3; Keep the retainer 5 at cone roller 4 interval; The oil sealing box 6 in sealing both ends face and oil sealing 7.
The outer circumferential face of axletree 10, the part corresponding with the inner peripheral surface end 2a of inner ring 2 forms groove 10a.Thus, when can prevent to bend, the inner peripheral surface end 2a of inner ring 2 interferes.This also goes for multiple row roller bearing.
But multiple row cone roller bearing 1 holds because of the export-oriented oblique crank Z of the path side end being docking cone roller 4, so inner ring 2 is separation inner rings of two inner ring components docking.Further, pad is also had between 2 inner ring components.
Fig. 2 is the figure after being amplified the side of the S place, end-to-end joint part of Fig. 1 separation inner ring.As shown in Figure 2, the aperture surface of inner ring 2, its central part possesses the contacting part 2b being embedded in axletree 10; Its outer edge possesses the non-contact portion 2c be separated with axle from radial direction; The boundary portion of contacting part 2b and non-contact portion 2c possesses ridge line section 2d.When flexure occurs axletree 10, ridge line section 2d interferes axletree 10 in the same manner as the inner peripheral surface end of inner ring 2.Its result, the outer circumferential face of axletree 10 also has the possibility producing axle trace at the S place, end-to-end joint part of inner ring 2.
So, in order to prevent the generation of S place, end-to-end joint part axle trace, such as, as Japanese Unexamined Patent Publication 2004-84938 publication is recorded, being known to the shoulder 2e of the interface by cutting inner ring 2, reducing the method for ridge line section 2d surface pressure.
But, in order to prevent S place, end-to-end joint part inner ring 2 and the interference of axletree 10, being not only bearing end 2a, also groove being set at the outer circumferential face of the axletree 10 corresponding with end-to-end joint part S, very difficult viewed from the viewpoint of the processing cost of axletree 10.
Thus, in order to prevent the generation of S place, end-to-end joint part axle trace, as the method etc. that Japanese Unexamined Patent Publication 2004-84938 publication is recorded, must the mechanism preventing axle trace be set in multiple row cone roller bearing 1 side.But in the method that above-mentioned publication is recorded, the surface pressure reduction effect of ridge line section 2d is little, can not fully prevent axletree 10 from producing axle trace.
Further, as other example of the bearing of support railway Vehicle Axles, with reference to Fig. 3, the multiple row cone roller bearing 101 supporting railway vehicle axle 110 possesses: the inner ring 102 of the path side end docking of two inner ring components; Outer ring 103; Be configured at the multiple row cone roller 104 between inner ring 102 and outer ring 103; Keep the retainer 105 at cone roller 104 interval; The Sealing 106 in sealing both ends face.
Fig. 4 is the figure after being amplified the side of P place, the end-to-end joint part inner ring component of Fig. 3.As shown in Figure 4, the aperture surface of inner ring 102, central part possesses the embedding part 102a being embedded in axletree 110; Outer edge possesses inserts guide portion 102b; Embedding part 102a possesses ridge line section 102c with the boundary portion inserting guide portion 102b.
When flexure occurs axletree 110, such as shown in Figure 3, the upside of axletree 110 is bent into convex, bear tensile stress, downside is bent into concavity, when bearing compressive stress, exist between P portion place's axletree 110 and ridge line section 102c and produce abrasion, the outer circumferential face 110a of axletree 110 produces the anxiety of abrasion or axle trace.Further, fine wrinkle place produces stress and concentrates, and has the possibility of major accidents such as causing that axletree fractures.
So, in order to prevent the generation of P place, end-to-end joint part axle trace, such as, as Japanese Unexamined Patent Publication 2004-84938 publication is recorded, being known to the shoulder 102d by cutting inner ring 102 interface, reducing the method for ridge line section 102c surface pressure.
Fig. 5 is the enlarged view of the Q portion periphery of the cone of multiple row shown in Fig. 3 roller bearing 101.Thus, because inner ring 102 all contacts with the end face of bonnet 107, so utilize bonnet 107 to limit the displacement of multiple row cone roller bearing 101.
This is because axletree 110 is to when radially bending, multiple row cone roller bearing 101 can not follow the distortion of axletree 110, the reason of the pressure of contact surface increase of ridge line section 102c.Further, only by the shoulder 102d thin-walled property of the interface of inner ring 102, it is insufficient that surface pressure reduces effect.Thus, can say that the friction of ridge line section 102c and axletree 110 causes to wear and tear or the problem of generation of axle trace still exists.Further, this problem also likely occurs at inner ring 102 and the contact segment of cutting oil ring 108.
Summary of the invention
Therefore, the object of the invention is to, the roller bearing that the axle trace providing the interference can effectively avoiding inner ring and axle to cause occurs.
Therefore, other objects of the present invention are, provide can the friction effectively avoided between inner ring and axle cause wearing and tearing and axle trace occur bearing construction.
Roller bearing for the present invention, possesses: at least one end has the inner ring of lip part; Outer ring; Be configured at the roller between inner ring and outer ring.The lip part of inner ring, its end face side possesses the thinner wall section of radial thickness relative thin, and its center side possesses the relatively thick heavy section of radial thickness.The aperture surface of inner ring, its central part possesses the contacting part being embedded in axle, and its outer edge possesses the non-contact portion be separated with axle from radial direction, and the boundary position in contacting part and non-contact portion possesses ridge line section.Further, the axial width L from inner ring end face of thinner wall section 1, and from the axial distance L of inner ring end face to ridge line section 2, meet L 1> L 2relation.
As above-mentioned formation, by making the parts thinner comprising inner ring ridge line section, the surface pressure of ridge line section can be reduced.Its result, even if ridge line section interferes axletree, also can prevent the generation of axle trace.
Preferably be arranged on the axial depth of inner ring end face and described axial width L 1identical circumferential groove, forms thinner wall section.In addition, preferred inner ring possesses the otch be communicated with to circumferential groove from its aperture surface.
The effect of inner ring thin-walled property, also can obtain by forming circumferential groove at end face.In addition, by filling oiling agent at circumferential groove, oiling agent can be supplied via otch between inner ring aperture surface and axle.Therefore, preventing of axle trace can be expected, and the friction preventing effectiveness of the little flange end face of inner ring.
Preferably axially distance L 2for 1mm≤L 2≤ 5mm.The non-contact portion of inner ring aperture surface, plays function as insertion guide surface when inner ring being pressed into axletree.And if then non-contact face is little, reduce as the function inserting guide surface, when having a press-in, the bight of inner ring and axletree is interfered, and wheel or inner ring aperture surface produce the possibility of scar.On the other hand, when inner ring is pressed into axletree, because inner ring is expanded diametrically, if so non-contact portion is large, the surface pressure of ridge line section increases.Therefore, by taking above-mentioned formation, can guarantee that non-contact portion is as the function inserting guide surface.
Further, the radial thickness L of the ridge line section position of preferred thinner wall section 3, be 0.04≤L with the pass of inner ring internal diameter φ 3/ φ≤0.1.If L 3/ φ < 0.04, because the rigidity of thinner wall section is too low, the load that inner ring is born exceedes maximum allowable stress, becomes the reason of bearing breakage.On the other hand, if L 3/ φ > 0.1, the surface pressure being difficult to obtain ridge line section reduces effect.Therefore, by taking above-mentioned formation, while maintaining bearing intensity, the surface pressure that can obtain fully preventing axle trace from occurring reduces effect.
Multiple row cone roller bearing for the present invention, possesses: at least one end has lip part, the inner ring of 2 inner ring component docking; Outer ring; Be configured at the tapered roller between inner ring and outer ring.The lip part of inner ring component, its end face side possesses the thinner wall section of radial thickness relative thin, and its center side possesses the relatively thick heavy section of radial thickness.The aperture surface of inner ring, its central part possesses the contacting part being embedded in axle, and its outer edge possesses the non-contact portion be separated with axle from radial direction, and the boundary position in contacting part and non-contact portion possesses ridge line section.
Further, the axial width L from inner ring component end face of thinner wall section 1, and from the axial distance L of inner ring component end face to ridge line section 2, meet L 1> L 2relation.
The lip part of multiple row cone roller bearing end face, and the lip part of inner ring end-to-end joint part, make by above-mentioned the parts thinner comprising inner ring ridge line section, can form groove and reduce the surface pressure of ridge line section in axle.Its result, even if ridge line section interferes axletree, also can prevent the generation of axle trace.
The present invention, because the ridge line section surface pressure that can reduce inner ring aperture surface, even if so ridge line section interferes axletree, also can prevent the generation of axle trace.
Bearing construction for the present invention possesses: axle; Be embedded in the bearing inner race of axle; With the end contact of bearing inner race, be embedded in the abutting member of axle.The end face of abutting member, its radially inner side possesses contacting part, with the end contact of bearing inner race; Its radial outside possesses non-contact portion, from contacting part on the position axially retreated, not with the end contact of bearing inner race.Then, the radial width w of inner ring end face 1, with the radial width w of contacting part 2, there is w 2/ w 1the relation of≤0.5.
By taking above-mentioned formation, because the displacement that bearing inner race can not be undertaken to a certain degree by the restriction of abutting member, even if so bent axle, the increase of the pressure of contact surface of axletree and bearing inner race contact segment also can be suppressed.Its result, can suppress the generation by fricative wearing and tearing and axle trace.
The internal diameter size d of preferred bearing inner race and the radial dimension D of contacting part upper end, has the relation of D/d >=1.1.If increase the area in non-contact portion, the displacement width of bearing inner race also becomes large.Therefore the bending quantitative change being just axle is large, also can suppress the increase of the pressure of contact surface of axle and bearing inner race.
But, with non-contact portion area increase to ratio, the area of contacting part diminishes.If therefore the pressure of contact surface of bearing inner race and abutting member is excessive, the wearing and tearing between two components etc. are uncertain.So, by making the internal diameter size d of bearing inner race, being D/d >=1.1 with the size relationship of the radial dimension D of contacting part upper end, can solving the problem.
The bearing inner race of preferred non-contact portion upper end and the axially spaced-apart of abutting member are more than 0.5mm.Thus, conjugate even if bearing inner race follows the bending of axle, also can avoid the contact with abutting member.
The end face in non-contact portion, such as, parallel with the end face of contacting part.Thus, can with easy processing non-contact portions such as lathes.
Preferably at contacting part, bearing inner race and abutting member clip unlike material member contact.In addition, unlike material component, preferred hardness is lower than the material of bearing inner race and abutting member.By clipping the unlike material component of hardness lower than two components between inner ring and abutting member, even if pressure of contact surface increases, also can suppress by the wearing and tearing etc. caused that rub.
The present invention, because bearing can follow the bending deflection of axle, so can reduce the ridge line section surface pressure of inner ring aperture surface.Even if ridge line section can be obtained interfere axletree, the bearing construction that axle trace occurs also can be prevented.
Accompanying drawing explanation
Fig. 1 is the figure of the example representing the multiple row cone roller bearing supporting railway vehicle axle;
Fig. 2 is the enlarged view in the inner ring component flange portion of the cone of multiple row shown in Fig. 1 roller bearing;
Fig. 3 is the figure of other example representing the multiple row cone roller bearing supporting railway vehicle axle;
Fig. 4 is the enlarged view of the P portion periphery of bearing construction shown in Fig. 3;
Fig. 5 is the enlarged view of the Q portion periphery of bearing construction shown in Fig. 3;
Fig. 6 A is the plan view of the inner ring component of the multiple row cone roller bearing of a mode of execution for the present invention;
Fig. 6 B is the sectional side view of the inner ring component of the multiple row cone roller bearing of a mode of execution for the present invention;
Fig. 7 is the enlarged view of the lip part of the inner ring component of Fig. 6 A and the multiple row cone roller bearing shown in Fig. 6 B;
Fig. 8 A is the plan view of the inner ring component of the multiple row cone roller bearing of other mode of executions for the present invention;
Fig. 8 B is the sectional side view of the inner ring component of the multiple row cone roller bearing of other mode of executions for the present invention;
Fig. 9 is the enlarged view in the inner ring component flange portion of Fig. 8 A and the multiple row cone roller bearing shown in Fig. 8 B;
Figure 10 is to confirm this invention effect, as the enlarged view in the inner ring component flange portion of the multiple row cone roller bearing of comparative example use;
Figure 11 is the ridge line section surface pressure representing inner ring and inner ring for the present invention in the past, the chart of the result obtained with finite element method;
Figure 12 is the figure of the bearing construction representing a mode of execution for the present invention;
Figure 13 is the amplification profile of the R portion periphery representing Figure 12, represents the state that the end face of contacting part and the end face in non-contact portion are formed abreast;
Figure 14 is the amplification profile of the R portion periphery representing Figure 12, represents that the end face in non-contact portion is the state of cone shape;
Figure 15 is the amplification profile of the R portion periphery representing Figure 12, represents that the end face in non-contact portion is the state of curve form.
Embodiment
The cone roller bearing of a mode of execution for the present invention, identical with the multiple row cone roller bearing 1 shown in Fig. 1, possess: two ends have the inner ring of the path side end face docking of two inner ring components of lip part; Outer ring; Be configured at the multiple row cone roller between inner ring and outer ring; Keep the retainer at cone roller interval; The oil sealing box in sealing both ends face and oil sealing, and be that the export-oriented oblique crank Z that the path side end of cone roller docks is held.
For the inner ring component 11 of this multiple row cone roller bearing, as shown in Fig. 6 A, Fig. 6 B and Fig. 7, its end face 12 side possesses the thinner wall section 13 of radial thickness relative thin, and center side possesses the relatively thick heavy section of radial thickness 14; In aperture surface, its central part possesses the contacting part 15 being embedded in axletree, and its outer edge possesses the non-contact portion 16 be separated with axle from radial direction, and contacting part 15 possesses ridge line section 17 with the boundary position in non-contact portion 16.
Further, the axial width L of the end face 12 to inner ring component 11 of thinner wall section 13 1, with the axial distance L till end face 12 to the ridge line section 17 from inner ring component 11 2, meet L 1> L 2relation.
As said structure, by making the parts thinner of the ridge line section 17 comprising lip part, groove can be formed in axletree and reducing the surface pressure of ridge line section 17.Its result, even if ridge line section 17 interferes axletree, also can prevent the generation of axle trace.
In particular, the scope setting axial distance is 1mm≤L 2≤ 5mm.The non-contact portion 16 of inner ring aperture surface, has the function as insertion guide surface when inner ring being pressed into axletree.Thus if non-contact face 16 is little, reduce as the function inserting guide surface, the bight that there is inner ring and axletree during press-in is interfered, wheel or inner ring aperture surface generation scar anxiety.On the other hand, when inner ring is pressed into axletree, because inner ring is expanded diametrically, if so non-contact portion 16 is large, then the surface pressure of ridge line section 17 increases.Therefore, by taking said structure, can guarantee that non-contact portion 16 is as the function inserting guide surface.
In addition, the radial thickness L of ridge line section 17 position of thinner wall section 13 3, be set in 0.04≤L with the relation of inner ring internal diameter φ 3in the scope of/φ≤0.1.If L 3/ φ < 0.04, because the rigidity of thinner wall section 13 is too low, so the load of inner ring 11 load exceedes maximum allowable stress, becomes the reason of bearing breakage.On the other hand, if L 3/ φ > 0.1, the surface pressure being difficult to obtain ridge line section 17 reduces effect.Therefore, by taking said structure, while maintaining bearing intensity, enough surface pressures that can obtain preventing axle trace from occurring reduce effect.
In addition, ridge line section 17 possesses fillet by fillet processing.And fillet processing department, preferably possesses the curvature of more than radius 1mm.Thus, be just that ridge line section 17 interferes axletree, concentrate because stress can be relaxed, so the generation of axle trace more effectively can be prevented.
Below, with reference to Fig. 8 A, Fig. 8 B and Fig. 9, the inner ring component 21 of the multiple row cone roller bearing being used for other mode of executions of the present invention is described.
The lip part of inner ring component 21, in end face 22 side by formed from end face 22 degree of depth be vertically L 1circumferential groove 23 and form thinner wall section, center side formed heavy section 24.In addition, identical with Fig. 6 A and Fig. 6 B, possess in aperture surface: contacting part 25; Non-contact portion 26, is positioned at the end face 22 of inner ring component 21 at axial distance L 2the ridge line section 27 of position.L herein 1, L 2pass be L 1> L 2.
Like this, by arranging circumferential groove 23 at end face 22, identical with thin-walled property, the surface pressure of ridge line section 27 can be reduced.
In particular, identical with above-mentioned mode of execution, setting axial distance L 2scope be 1 ~ 5mm, and/or be provided with the wall thickness L of radial direction of ridge line section 27 position playing circumferential groove 23 part of function as thinner wall section 3l is set in the relation of inner ring internal diameter φ 3in the scope of/φ=0.04 ~ 0.1, thus, the surface pressure that can obtain preventing axle trace from occurring fully reduces effect.
Further, identical with above-mentioned mode of execution, ridge line section 27 possesses fillet by fillet processing.And fillet processing department, preferably possesses the curvature of more than radius 1mm.Thus, be just that ridge line section 27 interferes axletree, concentrate because stress can be relaxed, so the generation of axle trace more effectively can be prevented.
On the inner ring component 21 shown in Fig. 8 A and Fig. 8 B, because be provided with the otch 28 communicated with circumferential groove 23 from its aperture surface, so by filling oiling agent in circumferential groove 23 inside, oiling agent can be supplied via otch 28 between inner ring aperture surface and axletree.Thus, can prevent the axle trace of axletree from producing, and the generation of friction of the little flange end face of inner ring can be suppressed.
In addition, in Fig. 8 A and Fig. 8 B, illustrate the example that otch 28 is set in four positions of inner ring aperture surface, but be not limited thereto, the otch 28 of any amount can be set.
The present invention goes for the path side end of inner ring, also goes for the large footpath side end of inner ring.In addition in the respective embodiments described above, the two ends illustrating inner ring component possess the example of lip part.As long as at least side has the inner ring component of lip part just can use.
In the respective embodiments described above, illustrate the example this invention being applicable to multiple row cone roller bearing, also go for multiple row roller bearing.Further, be not limited to multiple row, also go for single-row cone roller bearing or roller bearing.
Further, in the respective embodiments described above, the example that the export-oriented oblique crank Z illustrating the path side end docking of cone roller holds.But be not limited only to this, also go for positive combination (hereinafter referred to as " interior the synform ") bearing of the large footpath side end docking of cone roller.Now, because the general interior inner ring held to oblique crank Z is one, so the present invention is applicable to the ridge line section of inner ring end.
Then, in order to confirm effect of the present invention, utilize finite element method to obtain to bend the ridge line section 2d of the inner ring in the past 2 shown in (1) Fig. 2 when occurring; (2) ridge line section 17 of the inner ring component 11 of the mode of execution for the present invention shown in Fig. 7; (3) surface pressure of the ridge line section 37 of the inner ring component 31 shown in Figure 10.
Figure 10 is the enlarged view of the lip part of the inner ring component 31 of cone roller bearing, is used for making comparisons with the inner ring component 11 of the mode of execution for the present invention shown in the inner ring 2, Fig. 7 in the past shown in Fig. 2.
Possess in the aperture surface of the inner ring component 31 shown in Figure 10: contacting part 35; Non-contact portion 36; Be positioned at the ridge line section 37 on contacting part 35 and border, non-contact portion 36.
This inner ring component 31, from end face 32 to the distance of ridge line section 37, compares with the inner ring 2 in the past shown in Fig. 2, short by about 1/5.In addition, compared with the inner ring component 11 shown in Fig. 7, end face 32 periphery does not arrange thinner wall section.
In addition, produce the surface pressure of axle trace, consider and resolve error etc., be decided to be 140 [MPa].Figure 11 represents an example of result of calculation.
With reference to Figure 11, only have the surface pressure of inner ring ridge line section 2d in the past, significantly higher than the threshold value 140 [MPa] that axle trace occurs.Further, the surface pressure of the ridge line section 17 of inner ring component 11 for the present invention, compared with the ridge line section 2d of inner ring 2 in the past, reduces more than 70%.
Confirm thus, by making ridge line section be positioned at thinner wall section (such as, with shown in Fig. 4 and Fig. 5 of such as Japanese Unexamined Patent Publication 2004-84938 publication, ridge line section is positioned at outside thinner wall section to be compared), larger surface pressure can be obtained and reduce effect.
Also confirm in addition, the inner ring component 31 as shown in Figure 10 of using as comparative example, by making ridge line section 37 close to end face 32, also can obtain surface pressure and reducing effect.
Referring to Figure 12, the bearing construction about an embodiment of the invention is described.
Bearing construction shown in Figure 12 possesses: multiple row cone roller bearing 111, and it supports railway vehicle axle 120; Bonnet 117 and section oil ring 118, it abuts with multiple row cone roller bearing 111, as the abutting member being fixed on axletree 120.
Multiple row cone roller bearing 111 possesses: the inner ring 112 of the path side end docking of 2 inner ring components; Outer ring 113; Be configured at the multiple row cone roller 114 between inner ring 112 and outer ring 113; Keep the retainer 115 at cone roller 114 interval; The Sealing 116 at stuffing box bearing two ends, and be cone roller 114 path side end docking export-oriented oblique crank Z hold.
Figure 13 is the enlarged view of the R portion periphery of Figure 12 in addition, but the end face of the bonnet 117 relative with the end face of inner ring 112 possesses contacting part 117a at its radially inner side, with the end contact of inner ring 112; Its radial outside, possessing non-contact portion 117b from contacting part 117a to the position axially retreated, not with the end contact of bearing inner race 112.Further, the radial width w of inner ring 112 end face 1, with the radial width w of contacting part 117a 2, there is w 2/ w 1the relation of≤0.5.
By taking above-mentioned formation, because the displacement that inner ring 112 can not be undertaken to a certain degree by the restriction of bonnet 117, even if so axletree 120 bends, the increase of axletree 120 and the surface of contact pressure of inner ring 112 contact segment also can be suppressed.Its result, can suppress the generation by fricative wearing and tearing and axle trace.
In addition as shown in figure 13, the internal diameter size d of inner ring 112 1with the radial dimension D of contacting part 117a upper end 1, there is D 1/ d 1the relation of>=1.1.If increase the area of non-contact portion 117b, the displacement width of inner ring 112 also becomes large, be therefore just the bending quantitative change of axle 120 large time, also can suppress the increase of axle 120 and the pressure of contact surface of inner ring 112.
But, because with non-contact portion 117b area increase to ratio, the area of contacting part 117a diminishes, if so inner ring 112 is excessive with the pressure of contact surface of bonnet 117, the wearing and tearing between two components etc. are uncertain.So, by making the internal diameter size d of inner ring 112 1, with the radial dimension D of contacting part 117a upper end 1pass be D 1/ d 1>=1.1, can solve the problem.
Further, the inner ring 112 of non-contact portion 117b upper end and the axially spaced-apart δ of bonnet 117 1, be δ 1>=0.5mm.Thus, conjugate even if inner ring 112 follows the bending of axletree 120, also can avoid the contact with bonnet 117.
The end face of non-contact portion 117b, parallel with the end face of contacting part 117a as shown in figure 13.This non-contact portion 117a has the advantage can carrying out being easy to lathe etc. processing.But when axletree 120 bends very large, the end face of inner ring 112 has the possibility contacted with the bight 117c of non-contact portion 117b.Now, because the pressure of contact surface change of contact segment is very high, so the end face of inner ring 112 has the possibility that wearing and tearing occur.
So, as shown in figure 14, inner ring 122 also can be made to be tabular surface with the contacting part 127a of bonnet 127, non-contact portion 127b to be formed as the cone shape stretched to radial outside.Can also as shown in figure 15, make inner ring 132 be tabular surface with the contacting part 137a of bonnet 137, non-contact portion 137b is convex spherical shape.In any one mode of execution of Figure 14 and Figure 15, be just that inner ring end face contacts with non-contact portion, because the pressure of contact surface of contact segment is little, also can suppress the wearing and tearing etc. of inner ring end face.
Further, in the mode of execution of Figure 14 and Figure 15, although the inner ring at place of non-contact portion and the axially spaced-apart of bonnet are not fixed, in the upper end portion in non-contact portion, preferably δ is met respectively 2>=0.5mm and δ 3>=0.5mm.Further, the ratio of the radial width of inner ring end face and the radial width of contacting part, and the ratio of the internal diameter size of inner ring and the radial dimension of contacting part upper end are identical with the mode of execution shown in Figure 13.
Utilize the bearing construction in the past shown in Fig. 3 ~ Fig. 5, and the bearing construction of the mode of execution for the present invention shown in Figure 12 and Figure 13, carry out the test confirming effect of the present invention, obtain the result shown in table 1.
Table 1
Table 1 effect validation test result
Thus, in product in the past, at 110a place, the axletree corresponding with the path side ridge line section 102c of inner ring 102 surface, confirm the generation of axle trace.On the other hand, there is not axle trace more than 1000 hours in product of the present invention yet.From above results verification, the present invention can suppress the generation of wearing and tearing and the axle trace caused by rubbing.
Further, at contacting part, inner ring and bonnet also can clip unlike material member contact.Herein, as unlike material component, hardness can be used lower than the material of inner ring and bonnet.Such as, can the soft metals such as Cuprum alloy be used, or the resin such as the fluorine element resin with self lubricity, the porous materials such as the agglomerated material containing alloy.Thus, even if the pressure of contact surface of bearing inner race and abutting member increases, also can suppress between two components by the abrasion etc. caused that rub.
In the above-described embodiment, example the present invention being applicable to multiple row cone roller bearing is illustrated.But be not limited thereto, no matter also go for four-point contact ball, angular contact thrust ball bearing, deep groove ball bearings, roller bearing, self-aligning roller bearing, fluid bearing etc., be that rolling bearing or sliding bearing can be suitable for.
In addition, in the above-described embodiment, illustrate the example that contacting part and non-contact portion are set in the abutment portion of inner ring and bonnet, but also go for inner ring and cut the abutment portion of oil ring.
Above, describe embodiments of the present invention with reference to figure, but the present invention is not limited to illustrated mode of execution.Can to illustrated mode of execution, in the scope identical with the present invention or in the scope of equalization, various finishing and distortion in addition.
Industrial utilizability
The present invention can be well used in roller bearing and the bearing construction of the axle supporting the large bending moment effect such as railway vehicle axle.

Claims (4)

1. a bearing construction, it possesses:
Axle;
Bearing inner race, it is embedded in described axle;
Abutting member, it is connected to the end face of described bearing inner race, and is embedded in described axle,
The end face of described abutting member has the contacting part with the end contact of described bearing inner race at its radially inner side;
At its radial outside, from the position that described contacting part retreats vertically, have not with the non-contact portion of the end contact of described bearing inner race,
The radial width w of the end face of described bearing inner race 1, with the radial width w of described contacting part 2, have
w 2/w 1≤0.5
Relation,
At described non-contact portion upper end, the axially spaced-apart of described bearing inner race and described abutting member is more than 0.5mm,
The feature of described bearing construction is,
Described non-contact portion is formed as the cone shape stretched to radial outside.
2. bearing construction as claimed in claim 1, wherein,
The internal diameter size d of described bearing inner race
Radial dimension D with described contacting part upper end, has
D/d≥1.1
Relation.
3. bearing construction as claimed in claim 1, wherein,
At described contacting part, described bearing inner race and described abutting member contact with accompanying unlike material component.
4. bearing construction as claimed in claim 3, wherein,
Described unlike material component hardness compared with described inner ring and described abutting member is low.
CN201110200275.6A 2005-04-18 2006-04-05 Bearing construction Active CN102401011B (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2005119594A JP2006300130A (en) 2005-04-18 2005-04-18 Bearing structure
JP2005-119594 2005-04-18
JP2005122812A JP4731198B2 (en) 2005-04-20 2005-04-20 Roller bearing
JP2005-122812 2005-04-20
CN2006800128846A CN101160474B (en) 2005-04-18 2006-04-05 Roller bearing and bearing structure

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
CN2006800128846A Division CN101160474B (en) 2005-04-18 2006-04-05 Roller bearing and bearing structure

Publications (2)

Publication Number Publication Date
CN102401011A CN102401011A (en) 2012-04-04
CN102401011B true CN102401011B (en) 2016-03-09

Family

ID=37214631

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201110200275.6A Active CN102401011B (en) 2005-04-18 2006-04-05 Bearing construction

Country Status (4)

Country Link
US (1) US8636420B2 (en)
EP (2) EP1873411B1 (en)
CN (1) CN102401011B (en)
WO (1) WO2006115003A1 (en)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2851315A (en) * 1954-06-17 1958-09-09 Timken Roller Bearing Co Breathing bearing-seal
EP0697533A1 (en) * 1994-08-18 1996-02-21 The Timken Company Compact bearing and stiffened journal

Family Cites Families (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1927534A (en) * 1931-07-16 1933-09-19 Timken Roller Bearing Co Roller bearing for rocker arms and the like
US3672735A (en) * 1970-08-20 1972-06-27 Timken Co Bearing housing
US3741614A (en) * 1971-08-27 1973-06-26 Timken Co Roller bearings
IT1182697B (en) * 1985-11-22 1987-10-05 Riv Officine Di Villar Perosa TAPER ROLLER BEARING PARTICULARLY FOR RAILWAY USE
JPH05187438A (en) * 1991-07-10 1993-07-27 Matsuura Kikai Seisakusho:Kk Roller bearing
JPH0530558A (en) 1991-07-19 1993-02-05 Nippon Telegr & Teleph Corp <Ntt> Frequency division/time division type comosite multiplex optical switch
JPH0530558U (en) * 1991-09-30 1993-04-23 エヌテイエヌ株式会社 Lubricator for cylindrical roller bearing
DE4206764A1 (en) * 1992-03-04 1993-09-23 Skf Gmbh SEALED FOUR-ROW Tapered Roller Bearing, especially for working rolls of rolling mills
US5492419A (en) * 1994-07-19 1996-02-20 Ntn Corporation Cartridge axle pinion bearing assembly
US6033117A (en) * 1995-12-19 2000-03-07 Smith International, Inc. Sealed bearing drill bit with dual-seal configuration
US5588752A (en) * 1996-03-04 1996-12-31 Brenco, Incorporated Bearing and journal assembly
JPH11182560A (en) * 1997-12-16 1999-07-06 Koyo Seiko Co Ltd Rolling bearing device
NL1008681C2 (en) * 1998-03-23 1999-09-24 Skf Eng & Res Centre Bv Train bearing unit with improved anti-frictional corrosion behavior.
JP4019513B2 (en) * 1998-08-18 2007-12-12 日本精工株式会社 Railway vehicle bearing device
JP2001027254A (en) * 1999-07-15 2001-01-30 Ntn Corp Bearing unit for rolling stock
US6126321A (en) * 1999-07-16 2000-10-03 Brenco Incorporated Shaft journal bearing and seal wear ring assembly
JP3529691B2 (en) 2000-03-13 2004-05-24 株式会社不二越 Axle bearing device
US6293704B1 (en) * 2000-03-21 2001-09-25 The Timken Company Shaft mounting with enhanced stability
JP4076708B2 (en) 2000-06-13 2008-04-16 Ｎｔｎ株式会社 Railway vehicle bearing device
GB0107616D0 (en) * 2001-03-27 2001-05-16 Hansen Transmissions Int Profiled roller bearing
JP2003004035A (en) * 2001-04-17 2003-01-08 Nsk Ltd Bearing device
US6786645B2 (en) * 2001-11-21 2004-09-07 The Timken Company Mounting for vehicular road wheel
JP2004011715A (en) 2002-06-05 2004-01-15 Nsk Ltd Double row bearing for rolling stock axle
JP2004084938A (en) 2002-06-27 2004-03-18 Nsk Ltd Rolling bearing
JP2005273796A (en) * 2004-03-25 2005-10-06 Koyo Seiko Co Ltd Bearing device for supporting pinion shaft

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2851315A (en) * 1954-06-17 1958-09-09 Timken Roller Bearing Co Breathing bearing-seal
EP0697533A1 (en) * 1994-08-18 1996-02-21 The Timken Company Compact bearing and stiffened journal

Also Published As

Publication number Publication date
EP1873411B1 (en) 2011-06-15
EP2345821A1 (en) 2011-07-20
EP1873411A1 (en) 2008-01-02
CN102401011A (en) 2012-04-04
US20090028484A1 (en) 2009-01-29
EP1873411A4 (en) 2009-11-11
WO2006115003A1 (en) 2006-11-02
EP2345821B1 (en) 2012-12-26
US8636420B2 (en) 2014-01-28

Similar Documents

Publication Publication Date Title
WO2010007979A1 (en) Pressed cage, self-aligning roller bearing, and method of manufacturing pressed cage
EP2952763B1 (en) Multipoint contact ball bearing
JP6798780B2 (en) Tapered roller bearing
CN101160474B (en) Roller bearing and bearing structure
JPH02180314A (en) Roller bearing holder
CN100375853C (en) Radial roller bearing
CN116134252A (en) Seal stack assembly
CN102401011B (en) Bearing construction
EP1295654B1 (en) Method of manufacturing hub unit for supporting wheel and die for manufacturing the same
JP2006194320A (en) Method of manufacturing roller bearing and roller bearing
JP2010043734A (en) Pressed cage and roller bearings such as self-aligning roller bearing
JP2006105320A (en) Tapered roller bearing
JP4817985B2 (en) Thrust roller bearing
JP2005163873A (en) Rolling bearing
JP3200125U (en) Angular contact ball bearings
JP4731198B2 (en) Roller bearing
CN108591272A (en) A kind of dissection type aligning roller bearing retainer and its self-aligning roller bearing
CN110382891A (en) The planetary gear mechanism supporting structure of needle rollers with retainer and the needle rollers with this with retainer
JP2005299702A (en) Automatic aligning roller bearing
JP2018112220A (en) Spacer member, and bearing device for axle having the same
CN110382887A (en) The planetary gear mechanism supporting structure of needle rollers with retainer and the needle rollers with this with retainer
CN101737428A (en) Bearing cage structure
JP4668846B2 (en) Thrust roller bearing
JP2024022880A (en) bearing
JP2005257034A (en) Method of manufacturing hub unit for supporting wheel

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant